A six-speed transmission with fixed shaft and planetary compound transmission

Abstract

The invention discloses a six-speed transmission with a fixed shaft and planetary compound transmission, comprising a first intermediate shaft, a second intermediate shaft, a linkage shaft III and an output shaft IV; idler gears {1, 2, 3, 4, 6, 9, 10} and fixed gears {5, 7, 8, 11}, clutches {C1, C2, C3, C4, C5} and a planetary row. The scheme takes into account the advantages and disadvantages of fixed shaft transmission and planetary transmission, and combines with actual engineering needs, adopts the form of fixed shaft and planetary compound transmission, designs a six-speed transmission with a relatively simple and compact structure, designs six gears that are all deceleration, discards useless direct gears, reverse gears, and overdrive gears, so that the core of the transmission is more streamlined and easier to control. The transmission has a small number of meshing times in the fixed shaft transmission part, and the four gears of the fixed shaft part are only meshed twice, and the two gears are meshed four times, so the power loss is less.

Description

Technical Field

[0001] The invention belongs to the technical field of mechanical transmission, and relates to a six-speed transmission with fixed shaft and planetary compound transmission. Background Art

[0002] Mechanical transmissions are divided into fixed-axis gear transmissions and planetary gear transmissions. Fixed-axis transmissions have a simple structure but are large in size, while planetary transmissions have a compact structure but are complex in process and high in cost.

[0003] At present, the transmission schemes used in the field of fracturing truck transmissions are mainly divided into pure fixed-axis type, pure planetary type, and fixed-axis and planetary mixed type. However, there are certain defects. Although the pure fixed-axis type has a simple structure and high reliability, the gearbox size is large and heavy; the pure planetary type, although the gearbox structure is compact and has a large load-bearing capacity, has a complex structure, is difficult to maintain, and has low reliability. In addition, the current mainstream fracturing truck transmission transmission scheme involves too many gears, about 8-9 gears, but due to actual working conditions, some of the gears are rarely used or even not used. The more gears there are, the more complicated the transmission scheme and gear switching will be. Summary of the invention

[0004] The purpose of the present invention is to provide a six-speed transmission with fixed-axis and planetary compound transmission to solve the shortcomings of the current existing engineering machinery transmissions.

[0005] The technical solution adopted by the present invention is as follows:

[0006] A six-speed transmission with fixed shaft and planetary compound transmission, comprising an input shaft, a first intermediate shaft, a second intermediate shaft, a linkage shaft and an output shaft; 7 idler gears and 4 fixed gears, 5 clutches and a planetary gear, wherein: the first intermediate shaft rotates coaxially with the input shaft,

[0007] The second idler gear and the third idler gear are fixedly connected together to form a double gear, the double gear sleeve is arranged on the first intermediate shaft and is fixedly connected to the input shaft, the second idler gear of the double gear is meshed with the first idler gear on the second intermediate shaft, the third idler gear of the double gear is meshed with the fourth idler gear on the linkage shaft, the sixth idler gear on the first intermediate shaft is meshed with the fifth fixed gear on the second intermediate shaft and the seventh fixed gear on the linkage shaft respectively, the eighth fixed gear on the first intermediate shaft is meshed with the ninth idler gear on the linkage shaft, and the eleventh fixed gear on the first intermediate shaft is meshed with the tenth idler gear on the second intermediate shaft;

[0008] The second intermediate shaft is provided with a first clutch and a third clutch, the driven ends of the first clutch and the third clutch are both fixedly connected to the fifth fixed gear, the driving end of the first clutch is fixedly connected to the first idler gear, the driving end of the third clutch is fixedly connected to the tenth idler gear, the first intermediate shaft is provided with a fourth clutch, the driving end of the fourth clutch is fixedly connected to the eighth fixed gear, the driven end of the fourth clutch is fixedly connected to the sixth idler gear, the linkage shaft is provided with a second clutch and a fifth clutch, the driven ends of the second clutch and the fifth clutch are both fixedly connected to the seventh fixed gear, the driving end of the second clutch is fixedly connected to the fourth idler gear, and the driving end of the fifth clutch is fixedly connected to the ninth idler gear;

[0009] The planetary gear row comprises a sun gear, planetary gears, a ring gear and a planet carrier; the sun gear, planetary gears, the ring gear and the planet carrier form an internally and externally meshing planetary gear row.

[0010] Furthermore, five clutches are wet friction clutches.

[0011] The transmission scheme adopts the form of fixed-axis transmission and planetary transmission in series, which can reflect the advantages of both transmission modes at the same time. Because the fixed-axis transmission has a simple structure, high reliability, and is easy to control the switching of its gears, the fixed-axis transmission is used at the high-speed end. The planetary transmission has a large load-bearing capacity and the characteristics of load diversion, and the torque transmitted by the transmission at the low-speed end is large, so the planetary transmission is used at the low-speed end. In addition, at the input end, a double-toothed empty sleeve is used at the input end, and the input power is directly diverted to the second intermediate shaft and the linkage shaft through the double-toothed, and then converged to the sun gear, and finally output through the planetary carrier.

[0012] The first clutch, the second clutch, the third clutch, the fourth clutch and the fifth clutch are wet friction clutches, which have the advantages of smooth starting and reversing, large torque transmission, low wear and long service life.

[0013] In summary, due to the adoption of the above technical solution, the beneficial effects of the present invention are:

[0014] 1. Taking into account the advantages and disadvantages of fixed-axis transmission and planetary transmission, and combining with actual engineering needs, a six-speed transmission with a relatively simple and compact structure is designed in the form of fixed-axis and planetary compound transmission. Six gears are designed for deceleration, and useless direct gear, reverse gear, and overdrive gear are discarded, making the core of the transmission more streamlined and easier to control.

[0015] 2. The transmission has fewer engagement times in the fixed-axis transmission part, with only two engagements for the four gears and four engagements for the two gears, resulting in less power loss.

[0016] 3. For high-speed and heavy-load transmission, the output torque of the transmission at the end will be greater. With the help of the load distribution and large carrying capacity of the planetary transmission, a planetary transmission structure is adopted at the end. BRIEF DESCRIPTION OF THE DRAWINGS

[0017] In order to more clearly illustrate the technical solutions of the embodiments of the present invention, the following briefly introduces the drawings required for use in the embodiments. It should be understood that the following drawings only illustrate certain embodiments of the present invention and should not be regarded as limiting the scope. For those skilled in the art, other related drawings can be obtained based on these drawings without creative work, among which:

[0018] Figure 1 It is a schematic diagram of the transmission scheme of the present invention;

[0019] Markings in the figure: I-first intermediate shaft, II-second intermediate shaft, III-linkage shaft, IV-output shaft, S-sun gear, R-ring gear, PC-planet carrier, P-planetary gear, 1-first idler gear, 2-second idler gear, 3-third idler gear, 4-fourth idler gear, 6-sixth idler gear, 9-ninth idler gear, 10-tenth idler gear, 5-fifth fixed gear, 7-seventh fixed gear, 8-eighth fixed gear, 11-eleventh fixed gear, C1-first clutch, C2-second clutch, C3-third clutch, C4-fourth clutch, C5-fifth clutch. DETAILED DESCRIPTION

[0020] In order to make the purpose, technical scheme and advantages of the present invention more clearly understood, the present invention is further described in detail below in conjunction with the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are only used to explain the present invention and are not used to limit the present invention, that is, the embodiments described are only part of the embodiments of the present invention, rather than all of the embodiments. The components of the embodiments of the present invention described and shown in the drawings herein can be arranged and designed in various different configurations.

[0021] Therefore, the following detailed description of the embodiments of the present invention provided in the accompanying drawings is not intended to limit the scope of the invention claimed for protection, but merely represents selected embodiments of the present invention. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without making creative work are within the scope of protection of the present invention.

[0022] It should be noted that relational terms such as "first" and "second" are used only to distinguish one entity or operation from another entity or operation, and do not necessarily require or imply any such actual relationship or order between these entities or operations. Moreover, the terms "include", "comprise" or any other variants thereof are intended to cover non-exclusive inclusion, so that a process, method, article or device including a series of elements includes not only those elements, but also other elements not explicitly listed, or also includes elements inherent to such process, method, article or device. In the absence of further restrictions, the elements defined by the sentence "comprise a ..." do not exclude the existence of other identical elements in the process, method, article or device including the elements.

[0023] The features and performance of the present invention are further described in detail below in conjunction with the embodiments.

[0024] Embodiment 1

[0025] A preferred embodiment of the present invention provides a six-speed transmission with a fixed shaft and a planetary compound transmission, which is a transmission with all gears being a reduction gear, without a direct gear, an overdrive gear and a reverse gear. It is composed of a fixed shaft transmission part and a planetary transmission part, including an input shaft V, a first intermediate shaft I, a second intermediate shaft II, a linkage shaft III, an output shaft IV, a wet multi-plate friction clutch, namely, a first clutch C1, a second clutch C2, a third clutch C3, a fourth clutch C4, a fifth clutch C7, 7 idler gears, 4 fixed gears and a planetary gear.

[0026] The first intermediate shaft I is provided with the second idler gear 2, the third idler gear 3, the sixth idler gear 6, the eighth fixed gear 8 and the eleventh fixed gear 11, and the end of the shaft is provided with a sun gear S and a clutch C4. The second idler gear 2 and the third idler gear 3 are fixedly connected together to form a duplex gear, which is idle on the first intermediate shaft I. The second idler gear of the duplex gear is in constant mesh with the first idler gear 1 on the second intermediate shaft II, and the third idler gear 3 of the duplex gear is in constant mesh with the fourth idler gear 4 on the linkage shaft III. The sixth idler gear 6 is in constant mesh with the fixed gear 5 on the second intermediate shaft II and the seventh fixed gear 7 on the linkage shaft III, the eighth fixed gear 8 is in constant mesh with the ninth idler gear 9 on the linkage shaft III, the eleventh fixed gear 11 is in constant mesh with the tenth idler gear 10 on the second intermediate shaft II, and the sun gear S is in constant mesh with the planetary gear P in the planetary row.

[0027] The second intermediate shaft II has a fifth fixed gear 5, a first idler gear 1 and a tenth idler gear 10, a first clutch C1 and a third clutch C3. The first idler gear 1 is constantly meshed with the second idler gear 2 of the double gear on the first intermediate shaft I, the tenth idler gear 10 is constantly meshed with the eleventh fixed gear 11 on the first intermediate shaft I, and the fifth fixed gear 5 is constantly meshed with the sixth idler gear 6 on the first intermediate shaft I.

[0028] The linkage shaft III is provided with the sixth idler gear 4, the ninth idler gear 9, the seventh fixed gear 7, the second clutch C2 and the fifth clutch C5. The fourth idler gear 4 on the linkage shaft III is in constant mesh with the third idler gear 3 of the double gear on the first intermediate shaft I, the ninth idler gear 9 on the linkage shaft III is in constant mesh with the eighth fixed gear 8 on the first intermediate shaft I, and the seventh fixed gear 7 on the linkage shaft III is in constant mesh with the sixth idler gear 6 on the first intermediate shaft I. The output shaft IV is fixedly connected to the planet carrier PC, and the power is output from the shaft.

[0029] The planetary gear is composed of a sun gear S, a planetary gear P, a ring gear R, and a planet carrier PC. Power is always input from the sun gear S, output from the planet carrier PC, and the ring gear R is fixedly connected to the transmission housing.

[0030] When working: All clutches in this scheme are multi-plate wet friction clutches. When the clutch on a certain shaft is closed, the friction plate of the clutch is pressed tightly, and the idler gear on this shaft is fixed to the shaft as a whole, and there is no relative rotation between the shaft and the idler gear; when the clutch is disconnected, the friction plate is loosened, and the idler gear can rotate freely around the shaft.

[0031] Different transmission routes can be realized by opening and closing different clutches. According to the actual needs of the project, the gears realized by the six-speed transmission described in the present invention are all deceleration gears. The working conditions of the clutches in each gear and the power transmission route are described as follows.

[0032] In the first gear (F1), the first clutch C1 and the third clutch C3 are engaged, and the power passes through the second idler gear 2, the first idler gear 1, the fifth fixed gear 5, the tenth idler gear 10, the eleventh fixed gear 11 in sequence, and then is transmitted to the sun gear S and output from the planetary carrier.

[0033] In the second gear (F2), the first clutch C1 and the fourth clutch C4 are engaged, and the power passes through the second idler gear 2, the first idler gear 1, the fifth fixed gear 5, the sixth idler gear 6, the eighth fixed gear 8 in sequence, and then is transmitted to the sun gear S and output from the planetary carrier.

[0034] In the third gear (F3), the first clutch C1 and the fifth clutch C5 are engaged, and the power passes through the second idler gear 2, the first idler gear 1, the fifth fixed gear 5, the sixth idler gear 6, the seventh fixed gear 7, the ninth idler gear 9, the eighth fixed gear 8 in sequence, and then is transmitted to the sun gear S and output from the planetary carrier.

[0035] In the fourth gear (F4), the first clutch C2 and the third clutch C3 are engaged, and the power passes through the third idler gear 3, the fourth idler gear 4, the seventh fixed gear 7, the sixth idler gear 6, the fifth fixed gear 5, the tenth idler gear 10, and the eleventh fixed gear 11 in sequence, and then is transmitted to the sun gear S and output from the planetary carrier.

[0036] In fifth gear (F5), the second clutch C2 and the fourth clutch C4 are engaged, and the power is transmitted to the third idler gear 3, the fourth idler gear 4, the seventh fixed gear 7, the sixth idler gear 6, the eighth fixed gear 8 in sequence, and then transmitted to the sun gear S and output from the planetary carrier.

[0037] In the sixth gear (F6), the second clutch C2 and the fifth clutch C5 are engaged, and the power passes through the third idler gear 3, the fourth idler gear 4, the seventh fixed gear 7, the ninth idler gear 9, and the eighth fixed gear 8 in sequence, and then is transmitted to the sun gear S and output from the planet carrier. The above description is only a preferred embodiment of the present invention, and is not intended to limit the protection scope of the present invention. Any modification, equivalent substitution and improvement made by any person skilled in the art within the spirit and principle of the present invention shall be included in the protection scope of the present invention.

Claims

1. A six-speed transmission with fixed shaft and planetary compound transmission, characterized in that: It includes an input shaft (V), a first intermediate shaft (I), a second intermediate shaft (II), a linkage shaft (III) and an output shaft (IV); 7 loose gears and 4 fixed gears, 5 clutches and a planetary gear, wherein: the first intermediate shaft (I) rotates coaxially with the input shaft (V), The second idler gear (2) and the third idler gear (3) are fixedly connected together to form a double gear. The double gear sleeve is arranged on the first intermediate shaft (I) and is fixedly connected to the input shaft (V). The second idler gear (2) of the double gear meshes with the first idler gear (1) on the second intermediate shaft (II). The third idler gear (3) of the double gear meshes with the fourth idler gear (4) on the linkage shaft (III). The sixth idler gear (6) on the first intermediate shaft (I) meshes with the fifth fixed gear (5) on the second intermediate shaft (II) and the seventh fixed gear (7) on the linkage shaft (III). The eighth fixed gear (8) on the first intermediate shaft (I) meshes with the ninth idler gear (9) on the linkage shaft (III). The eleventh fixed gear (11) on the first intermediate shaft (I) meshes with the tenth idler gear (10) on the second intermediate shaft (II). The second intermediate shaft (II) is provided with a first clutch (C1) and a third clutch (C3), the driven ends of the first clutch (C1) and the third clutch (C3) are fixedly connected to the fifth fixed gear (5), the driving end of the first clutch (C1) is fixedly connected to the first idler gear (1), the driving end of the third clutch (C3) is fixedly connected to the tenth idler gear (10), the first intermediate shaft (I) is provided with a fourth clutch (C4), the driving end of the fourth clutch (C4) is fixedly connected to the eighth fixed gear (8), the driven end of the fourth clutch (C4) is fixedly connected to the sixth idler gear (6), the linkage shaft (III) is provided with a second clutch (C2) and a fifth clutch (C5), the driven ends of the second clutch (C2) and the fifth clutch (C5) are fixedly connected to the seventh fixed gear (7), the driving end of the second clutch (C2) is fixedly connected to the fourth idler gear (4), and the driving end of the fifth clutch (C5) is fixedly connected to the ninth idler gear (9); The planetary gear row comprises a sun gear (S), a planetary gear (P), a ring gear (R) and a planet carrier (PC); the sun gear (S), the planetary gear (P), the ring gear (R) and the planet carrier (PC) form an internally and externally meshing planetary gear row.

2. A six-speed transmission with fixed-axis and planetary compound transmission according to claim 1, characterized in that: The five clutches are wet friction clutches.

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